Clutch and clutch control mechanism



April 21, 1953 Original Filed Oct. 15, 1945 i E. E. WEMP CLUTCH AND CLUTCH CONTROL MECHANISM IIIIIIIIIIIIIA 6 Sheets-Sheet 1 Brie-$23 @074 A ORNEYS April l953 E. E. WEMP CLUTCH AND CLUTCH CONTROL MECHANISM Original Filed Oct. 15, 1943 6 Sheets-Sheet 2 lllllli HHI INVENTOR v Zfi'ngst Z7 "4 07p A ORNEYG April 21, 1953 v E. E. WEMP 2 2 CLUTCH'AND CLUTCH CONTROL MECHANISM Original Filed 06's. 15, 1943 6 Sheets-Sheet 5 0/5 ENGAGEMENT ENG'A GENE/V T 5105 L0 ".IIIIIIIIIIIIII"..

i 45 a 44 5!! E 4/ a i 50 INVENTOR 77 Ernest Zi' M em A ril 21, 1953 E. E. WEMP v CLUTCH AND CLUTCH CONTROL MECHANISM 0riginal Filed Oct. 15, 1943 s Sheets-Sheet 4 INVENTOR 17 704.56 Z V F1141], VQI V y aw iTORNEYS April 21, 1953 E. E. WEMP 2,635,722

CLUTCH AND CLUTCH CONTROL MECHANISM Original Filed Oct. 15, 1945 s Sheets-Sheet 5 I IMHEUJP Mgawaf /zo /z z mm W 2 6 2 RW w 7, m a o o 2 5 h N R 3 S k. E n. V40 0 5 mg n 2 m m .A w O I 6 o Nw m5 0% utO O ms April 21, 1953 E E WEMP CLUTCH AND CLUTCH CONTROL MECHANISM Original Filed Oct. 15, 1945 Patented Apr. 21, 1953 CLUTCH AND CLUTCH CONTROL MECHANISM Ernest E. Wemp, Detroit, Mich.; William O'Neill Kronner and Lila A. Wemp, executors of said Ernest E. Wemp, deceased Original application October 15, 1943, Serial No.

506,402, now Patent No. 2,479,532, dated August 16, 1949.

Divided and this application May 4, 1949, Serial No. 91,294

9 Claims.

This invention has to do with the transmission of power from a power source to driven means, where the torque line is to be interrupted at times for one purpose or another and then re-established. The invention is concerned particularly with an arrangement for the transmission of power from an engine in an automotive vehicle where the engine is to be disconnected from the traction wheels of the vehicle for the changing of gears to effect different driving ratios and to permit the engine to run while the vehicle is at rest. 1

i This application is a division of co-pending application Serial No. 506,402, filed October 15, 1943, Patent No. 2,479,532, dated August 16, 1949.

The invention relates to what may be termed aclutch and clutch control arrangement wherein the clutch is engageable and disengageable for gear shifting purposes or the like. In accordance with the invention a centrifugal clutch is provided which is designed to be disengaged at engine idling speeds but which becomes engaged upon acceleration of the engine above idling speeds. Thus the clutch is of an automatic nature The engine referred to in the specific disclosure herein is an internal combustion engine which may be of the usual and well known type. In conjunction with the centrifugal clutch, are means for effecting clutch control and for supplementing the clutch packing pressure. In this connection the centrifugal clutch is relatively lightly centrifugally weighted so that the clutch, when acting under centrifugal force alone, is not capable of transmitting full engine torque until the engine has reached a fairly high R. P. M. The means for supplementing the clutch packing pressure is preferably a hydraulic arrangement, operable from a driven member, 1. e. a member which operates only upon movement of the vehicle.

One of the objects of the invention is to provide an arrangement wherein the centrifugal clutch is disengaged at normal idling speed so that the engine may be running while the vehicle is at rest but which engages centrifugally upon acceleration of the engine above idling speed to initiate vehicle movement. The hydraulic system begins to function at a relatively low speed of movement of the vehicle. However, whenthe vehicle is decelerated the hydraulic system holds the clutch engaged at engine R. P. M. lower than the R. P. M. at which the clutch would disengage centrifugally. Therefore, the engine and the traction wheels remain coupled together uponthe deceleration of the vehicle below the speed at which the centrifugal clutch would otherwise become disengaged.

A further object of the invention is to providea nicety of clutch engagement which is afforded by the lightly weighted centrifugal clutch and wherein the packing pressure of the clutch is supplemented by the hydraulic system to provide adequate torque capacity at speeds lower than the speed where the centrifugal system is capable of providing clutch packing pressure suincient for transmitting full engine torque.

Another object is to provide an arrangement where the end thrust caused by the hydraulicv system is relieved at vehicle speeds at which vehicles quite usually are normally operated.

A further object of the invention is to provide a centrifugal clutch and a hydraulic control and pressure supplementing means wherein the hydraulic pressure is variable in a manner similar to the variation of centrifugal force with variation in R. P. M. It is of course well known that centrifugal force increases with the square of the speed; the hydraulic system advantageous.- ly embodies a pump arrangement functioning from centrifugal head and velocity head of the liquid, both of which increase with the square of the speed. Thus the pump constitutes both a? pump and pressure regulator. In other words, there is a pumping action upon vehicle move ment and the pressure. thereof varies with the square of the speed. This liquid pressure is em-' ployed to supplement the clutch packing pressure and to also release the clutch against centrifugal force at any speed of operation. Obviously, it takes more force to release the clutch against centrifugal action at high R. P. M. than it does at low R. P. M. but since the liquid pressure varies with the square of the speed as does the centrifugal force of the clutch, the pressure is adequate to disengage the clutch at any operclutch is disengaged. The manner of engagement.

of a clutch, however, cannot be disassociated from the relative engine and vehicle speeds. Some ope. erators operate the engine at a high R. P. M. just prior to clutch engagement, with the resultv there is considerable clutch slippage before the engagement is complete. Other operators attempt, more or less, to synchronize the engine R. P. M. with vehicle speed for a minimum of clutch slippage. In accordance with this last mentioned object of this invention, the control of the operation of the engine is automatically governed during the period of clutch disengagement and engagement. In other words, the automatic operation of the clutch is coordinated with an automatic control of the engine. To this end, the operator of a vehicle who desires to effect a change of gears performs a gear shifting action which results in automatic clutch disengagement, and before the clutch is disengaged the control of the throttle of the engine is taken over by the automatic means. In other words, the operation of the engine is taken out of the control of the driver and is governed by the clutch operating means. After the clutch has opened and the gear shift made, the driver, having completed the gear shift, discontinues the manual control and the clutch then begins to re-engage. When the clutch is sufficiently engaged the control of the throttle is released by the automatic means and restored to the driver. Thus it will be observed that the engine is not under the control of the driver during that period beginning in the disengaging action, continuing while the clutch is disengaged, and until the clutch is again at least partially engaged. Yet there is no dictation as to when an individual driver may make a shift of gears; this is left to the driver to exercise his ownideas and preferences of what may or may not be necessary to meet the exigencies of the situation. This phase of the invention will be better understood, as also will other objects of the invention when the detailed descriptionis considered in conjunction with the accompanying drawings which show one form'of apparatus for carrying out the invention in addition to a modified form of control.

Fig. 1 is a cross sectional view showing a centrifugal clutch and a liquid pump arrangement mounted in a bell housing associated with an internal combustion engine.

Fig. 2 is a sectional view taken substantially on line 22 of Fig. 1.

Fig. 3 is a rear elevational view of the centrifugal clutch.

Fig. 4 is a sectional view taken substantially on line 44 of Fig. 3 illustrating a clutch detail.

Fig. 5 Ban elevational view taken substantially on line 55 of Fig. 1 showing the pump structure and illustrating some of the parts in dotted lines.

Fig. 6 is an elevational View of the opposite side of the pump structure and taken substantially on line 6-6 of Fig. 1.

Fig. 7 is a sectional view taken substantially on line 'l'! of Fig. 6.

--Fig. 8 is a view of the clutch operatingcylinder shown in Fig. 12, looking from the right hand side of Fig. 12 and showing some of the passageways in dotted lines.

Fig. 9 is 'a side elevational view of the clutch or bell housing illustrating various control mechanism for the clutch and for the throttle of the engine.

Fig. '10 is a sectional view taken substantially on line Hll0 of Fig. 9.

Fig. 11 is an end view of theclutch housing showing some of the control mechanism mounted thereon and illustrating the piping of the hydraulic'system.

Fig. 12 is a sectional view taken through the clutch operating cylinder.

Fig. 13 is a sectional View taken through the cylinder in the throttle control system.

Fig. 14 is a sectional view taken through the solenoid valve of the hydraulic system showing the valve in clutch engagement position.

Fig. 15 is a sectional view similar to Fig. 14 showing the valve in clutch released position.

Fig. 16 is a sectional view through the manual control handle and taken at right angles to the illustration thereof in Fig. 14.

Fig. 17 is a sectional view taken substantially on line l'i-l 1 of Fig. 14.

Fig. 18 is a bracketed view of a number of inter-fitting parts in the control system illustrated in section in Fig. 10.

Fig. 19 is a view, largely in side elevation showing a modified form of engine throttle control.

Fig. 20 is a View similar to Fig. 11 showing in elevation the control cylinder and piping of the modified form.

In Fig. 1 an engine block is illustrated at'l. the crank shaft at 2 and the flywheel at 3 which is positioned within the clutch housing 4. A driven shaft 5 is piloted at one end in the wheel, as shown, and extends through the housing 4 and into a gear box 6 containing shiftable gears for varying the speed ratio between the driven shaft 5 and propeller'shaft l. The gears may be shifted through the means of a suitable shiftable element, such as a rodor the like 8.

The centrifugal clutch includes a cover plate Ii! bolted to the flywheel and a pressure plate H. The pressure plate and the: flywheel-are adapted to engage between them the facings 12 of a driven disc [3 mounted on the drivenshaft 5. The facings are normally held yieldable spaced apart by suitable yielding means M. A number of forms of such yielding means are Well known to those versed in the art.

Mounted on the cover plate are brackets-I1 (Fig. 4) which are attached to the inside of the cover plate, each of which has a pair of projections or ears [8 extending out through an opening in the cover plate as shown in Fig. 3. There are three of such brackets and themessure plate II has projecting tongues l9 which lie between the ears 18. Thus the pressure plate is drivingly associated with the cover plate and it can be shifted axially. The pressure plate normally retracted into a clutch disengaged position by springs 2%. As will later appear the action of the springs 2% may be supplemented by means located outside the housing. -A combined lever and centrifugal weight is mounted between each pair of projections I8 on ;a pin 22 advantageously through the means of needle roller bearingsas shown, and each has a weighted mass 23 and an inwardly extending lever arm 24 provided on its end with an involute tooth 25. Each weighted lever engages the adjacentprojecting tongue of the pressure plate as indicated at .26. It will be apparent that the. weighted masses provide an unbalanced condition so that upon rotation the levers are swung on their axes so 'thatthe lever arms 24 shift to the right as Fig. 1 is viewed and the pressure plate is pushed to the left and into engagement with thedriven disc.

A clutch control shaft 28 has a yoke w thereon, the ends of the arms of which are engaged with a control sleeve '30 through the-means of pin and slot connections 3| so that the'yoke m'ay shift the control sleeve in both directions. anti-friction bearing 32 connects the control sleeve with "a control sleeve part oreimexit aa havingai'i annular groove 34' for receiving the involute ends 25 of the clutch levers 24. It will be observed any rocking movement of the clutch levers must be accompanied by a reciprocating movement of the control sleeve and vice versa. As shown. in Fig. 3, there are three of the com bined weight and lever elements. 1

The pump shown herein is mounted in the housing 4 which is divided by a partition 35 to provide'a sump chamber 36. This pump comprises essentially two elements, namely, a shell or casing and Pitot tube mounted for relative rotation." The shell has one wall mounted on a hub 38- which is keyed to the driven shaft 5 while the other wall, which is axially spaced from the first wall, has a central opening39. A hub element 48 journalled on the drivenshaft has a radial extending arm 4|, on the end'of whichis a head 42. There is an opening T43 in the head which opens substantially tangentiallyand a passage 44 extending through-the arm and hub and to an outlet 45. An outlet pipe 46 connects at 45 and extends out through the wall of the housing 4 to an outlet fitting 4'! (Fig.9).

In the operation of the pump, the shell rotates and a quantity of the liquid is maintained therein which liquid, due to centrifugal force, forms an annular ring of liquid in the shell. The pressure at the inlet of the Pitot tube is represented by centrifugal head plus velocity head. The oil enters the passage and is caused to flow'through the outlet pipe. In the normal operation of the hydraulic system herein disclosed, there is no actual flow of liquid needed but a pressure must be maintained. When there is no flow through the Pitot tube channel, the oil in the shell merely flOWs past the Pitot tube and its head and as will be observed by reference to Fig. 5, the Pitot tube and its head are streamlined to minimize friction and resistance. The Pitot head is perfectly streamlined on its radius as illustrated. When the parts come to rest, some of the oil in the shell will be dumped but the oil will be maintained in the lower portion of the shell up to the level of the open ing 39. Upon the commencement of operation, this volume of oil issufficient to start the pump and supply the initial quantity of oil. To this end, it will be noted that the head of the Pitot tube is disposed near the periphery of the shell so", that it will be at all times submerged.

1 Suitable means may be provided to keep the shell full of oil during operation. One such means may take the form of a lift pump 'of the Archimedes spiral type. The structure may comprise two sheet metal plates 58and 5| placed face to face and secured to the hub at 52. The plate 5| is formed with two spiral grooves 53 and 54 which provide channels 55. These are open at their outer ends as at 56 where the plate 5| is provided with an aperture 51 and their inner ends communicate with inlet apertures leading into the shell as at 58. During rotation of the shell the channels lift the liquid and discharge the same into the shell and thus keep it full. A structure for keeping the shell full of oil by the operation system is shown in Fig. 1 herein. The partition 35 is provided with a trough formation 68, the lower end of which discharges oil into a formed groove 6| in the hub. In normal operation the oil in the sump is splashed and some of it falls into the trough 68 from where it flows through 6| into the shell. Thesetwo means for keepingthe shell-filled with oil may be used individually or together. The two Archimedes spirals are provided tokeep the.

plates in balance. a V

The control mechanism as shown in Fig. 9 in-,- cludes a clutch control cylinder 65 mounted on trunnions in bracket 66 so that it may rock in this cylinder (Fig. 12) is a piston 64 having a piston rod '61. This piston rod has a pin and, slot connection 68 with a control arm 69. The clutch shaft 28 has yoke member 18 keyed thereto while the arm 69, which is of bell crank form, has an arm 1| operably connected to the yoke 18. The yoke has two abutments 12 while a bolt 13 is screw threaded through the arm and it. has a nut 14 screw threaded on its opposite end. In this way the control arm 69 and the rock shaft are coupled together but the coupling can be adjusted. To make an adjustment the bolt 13 is turned on its screw threads in 'H thus changing the relative position of the control arm and the clutch rock-shaft. After the adjustment is made the nut 14 is adjusted to engage one of the abutments '12. It is easily understood thatv the head of the bolt and nut 14 engage the abutment 12 so that rocking of the arm 69 causes rocking of the clutch shaft. This adjustment is for clutch facing wear as will later appear.

I The pump outlet 41 is connected by a conduit: 11 to a solenoid valve generallyillustrated at 18. A conduit 19 extends from the valve and enters the cylinder 65 at 88 and connects to a passage, 8| which connects into the cylinder on the rod side of the piston (Figs. 8 and 12). A conduit 82 extends from the valve and enters the cylinder at 83 through passage 84 and into the cylinder on the side of the piston opposite the rod 61. By a suitable operation of the valve, the pressure liquid may be introduced into either side of the cylinder while connecting the otherside back to the sump. There is, what may be termed, an energizing cylinder 86 which is smaller than the cylinder 65 and a conduit 81 leads from the pump outlet 41 to one end of cylinder 86 as shown in Fig. 13. The piston 88 in this cylinder is acted upon by a spring 89 and it has a piston rod 98 with an adjustable connection 9| to an arm 92.? Whenever the pump is in operation, the liquid under pressure is transmitted into cylinder 86- and the piston 88 is shifted to the left hand end of the cylinder as Fig. 13 is viewed. 9

The cylinder 86 has to do with the control of the engine throttle, an arrangement now t0 'b&; described. The usual throttle treadleas shownat connects to the carburetor lever 96, through a link 91 and arms 98 and 99 mounted for rocking movement in unison, and a link or rod I88. When the treadle 95 is depressed, the throttle arm 96 is rocked toward open position or clock: wise as Fig. 9 is viewed. Rotatablewith the crank arms 98 and 99 is an arm I82 connected; by a link I83 with an arm I84 mounted on the-v clutch shaft 28.

, Means are provided for coupling the clutch shaft with the throttle control so that when the vehicle is moving and the clutch is disengaged the movements of the clutch governs throttle movement. To this end a coiled spring type of clutch is employed as shown in Fig. 10. .There is a sleeve |81 keyed to the control lever 69, as at, I88, and this sleeve has a flange I89 which is. cut away to provide an abutment ||8. There'is another interfitting sleeve positioned over the sleeve |8'| as illustrated at I I3 and it has a flange cut away to form an abutment 2, (Fi 1. The-sl ve 1 s c nn c e to the arm; .szan

assay-22g:

7 mdeed the 'a-rm -fl may constitute. -a part of a smallhousingl 15. Surrounding the two .interfitting sleeves is a coiled spring I16, theendsxof whichaare --fiared outwardly at I I1 and II 8 in such a. manner as to engage .:the :abutments I Ill and 1 I2.

Surrounding the spring IfIB .is'sleeve I20 with learance relative to the spring so that the sleeve is freely: rotatable relative to the :spring. This sleeve I 20; has a yi'elda'ble connection withthe arm IOL 'I his yieldable connection takes .the form of a torsion. spring YI2I,. one end which at l 2-2enga'ges the sleeve and theiotherend of which at 123 connects.'toiithe'ifiange 'of a sleeve I24 mounted: ni'the clutch shaft28 and. to which the arm"PIM i's. connected. iThereHis an additional coupling which may ibe termeda safety. coupling between sleeve-I6 and sleeve H3 and which takes the form of za 'pin I26 positionedin. a part of the sleeve ill-I and engaging in aslot I21 in the' sleeve 1 1.3. .The slot is considerably wider than the diameter of the pm .as will be seen by reference 'toFig. -18, thespurposes of which will presently appear.

"There single. operation required of the operation in the control of the entire mechanism, by means of which the action of :the clutch and therhydraulic system .is governed. This operation may be -associated and preferably is associated with the mechanism for shifting the gears in: the transmission through the means of the member 8. To this-end, as shown in Figs. 1 and 14, there is a movableelement 8a which may be directly connected W-ith'the-memberS for shifting the gears or connected thereto through suitable linkage (not shown). There is a handle or knob I30 connected to the member 8a yieldably as by means o'f coiled "spring I3l. The member 812 has an insulated electrical contact ferrule I32 for contact with the spring 131 and the spring is grounded as shown. An electrical conductor I34 connects to the solenoid; another electrical conductor I35 extends from thesolenoid to a battery or other source-of power I 36-which is groundedas at I31. 'Thus'when the spring contacts the member 132, the 'solenoidis' energized. The member 8a,=near its end and between the contact I 32 and the point of connection with the spring I'3I ,is of flattened construc'tion as shown-at "I38 (Fig. 17). Pressure applied by the-hand of the operatoron the *knob' in theplaneof the drawing inFig. 14 willnot-resultin'themaking of an electrical contact. Thus-thesection I38 supports the spring I'3 I. "However, pressure applied at right angles into or in the-plane of the drawings as Fig. 16 is viewed 'flexes the spring 'I'3I so that an electricalcontaot may be established. 'Thusan operator may allow his hand to :restupon the knob without making an'electrical contact. When the knob is pushed in any direction for shifting gears, the

' spring is' fiexed as shown in Fig. 16.

The solenoid for the valve is illustrated at I40 and the body of the valve MI may besecured directlyito the housing l. =Thevalve housing has the Ipressure inlet port TIato which the pressure line 11 connects and it has two ports in communication withtwo ports I-'42 andl43 connecting into thesump chamber. The ports in the valve body are shown as rectangular which is'an expedient formation of the ports in-such a 'valve and it willbe-understood the valve may be :a die'casting so that the ports maybe readily formed in such shape. '"The valve housing-also has two passages which'l'ead to the lines 19 and-82.

- arithmetic housine' i's avalve'member HS-acted 16 upon by a spring I 46. The valveymember'has. a port and a port I5:I defined by lands I52, I53 and I54. The valve alsohasa passage I55 passing therethrough from end to end and it has a circumferential groove I56 which is connected to the passage I55 by an axial port I51. The valve is in a position as shownin Fig. 14 which is a normal operating condition. .The pressure fluid from the pump enters at Ila, passes through port I50 into line 19 and into the engagement side of the control cylinder which is at the left hand side as shown in Fig. 12, and thus the piston rod 61 is retracted. At this time the pressure liquid in the opposite side of the control piston can escape into-the sump through line 82, port I5l and port I43. If there is any leakage past the land I52, the liquid enters the groove I56 and escapes through the port I42 into the sump. In the case of leakage past-the land I53 the liquid is returned to the sump through port I43. The valve itself is hydraulically balanced and any oil or liquid which may be trapped in the ends of the valve may flow through the axial passage I55 through radial port I5? into groove I56 and to the sump. When the solenoid is energized, the valve-I45 is lifted magnetically to the position shown in Fig. 15. In this position, the pressure liquid entering at I'Ia passes through port I5I, which is closed from the exhaust I43 and through line 82 to the opposite end of the control cylinder. The liquid in line I'Imay be discharge through port I50 and port I42 back to the sump. It is understood, of course, that the system remains full of liquid and the lines "I9 and 82 remain full of liquid and the only liquid discharged into the sump is that displaced by the movements of the control piston. It will be appreciated how shifting of the solenoid causes a shift of the control piston from one end of its cylinder to the other.

In order to provide an easily accessible and outside clutch adjustment, there is a. rod I60. which connects to a part of the control arm 69 at I6! and this rod extends through a suitable abutment I62 where it is provided with 'a pair of suitable stop nuts Iii-3. A spring I64 reacts against the stop I62 and a nut I65 screw threaded on the rod. Between the nut I65 and spring I is a washer I66 which is non-rotatablyimounted on the'rod I60-and the nut and washer "having-an interengagement at I61 comprising a recess in one and a teat on theother :so that'the nut may be turned for adjustment with a snap actionwith' respect to the washer for purposes which will presently appear.

In describing "the operation of the structure various additional functions of some of the parts will appear and'it is believedto be most ex edient to bring out these functions .in a consideration of the operation, so thatthe function will be better understood and appreciated. In a normal at rest condition of the vehicle with the engine idling; say at 500 01-600 R. PJM. the clutch is openasshown in Fig. 1. 'At this time, the driven shaft and the pump are not operating. 'The springs 20 hold the 'clutch'pressure plate retracted. Also the spring I54 pushes on rod I60 and-acts through the control arm '69, rock shaft 28 and through sleeve 36to swingthe clutch levers toward the left as'Fig. 1 is viewed. 'Thus the springs '20 and the outside spring I64 serve 'to hold the clutch disengaged under these circumstances. The'adjustable nuts 163 provide a'readily accessible outside adjustment for determining the amount'of pressure plate retraction, and "the; clearance in disengagement. Upon acceleration the centrifugal clutch trifugal force overcomes the action of the springs aces-722 begins to close as cen- 20 and the sprin I64. The point of engagement can be varied by adjusting the tension on the spring I64 through the means of the nut I65. This provides a readily accessible outside adjustment for this purpose. Initially the connection between the yoke 12 and the arm H (Fig. 9) is set up for new clutch facings and the adjustment at this point may be made from time to time to accommodate for facing wear. Upon acceleration, the centrifugal clutch will engage at a suitable R. P. M. above engine idling speed. The centrifugal weights as above mentioned are relatively light so that there is a smooth initial engagement and as soon as the driven shaft begins to rotate the pump begins to function.

' The pressure liquid is transmitted through the 'valve which is in the position as shown in-Fig. -14 through the line F9 to the engagement side'of the control piston which is the left hand side as shown in Fig. 12. Movement of the piston rocks the clutch control shaft clockwise as Fig.

9 is viewed (counterclockwise as Fig. 1 is viewed) and'exerts a pull on the clutch levers 24, thus tending to turn the clutch levers in a direction which aids and supplements centrifugal force. The centrifugal weights themselves may, for example, be arranged so as not to exert enough pressure to handle full engine torque until the engine is at about 2400 R. P. M., whereas the supple- -mental hydraulic force may be arranged toprovide such supplemental pressure that full'engine torque can be handled by the clutch at about 1 200 R. P. M. These figures are only exemplary. Upon deceleration of the vehicle, the centrifugal clutch in itself would disengage at a speed above. engineidlin speed or, for example, at about 700 or 800 R. P. M. But since the hydraulic system is functioning, the hydraulic pressure holds the clutch closed to a lower engine R. P. M. say, for example, about 300 R. P. M.

Thus, the vehicle can be slowed down and operated at a very low rate of speed. At this point the importance of the lost play between the clutch control piston and the clutch mechanism at .68 may be brought out. Force applied to the clutch levers through the sleeve 30 places an end thrust on the engine crank shaft. When the control cylinder has been shifted to the end of its clutch engagement stroke, which is the right hand end of the cylinder as shown in Fig. 12, it is stopped by the abutment as shown. At speeds, say, for example, above 2400 R. P. M., centrifugal force increases but no further movement occurs in the hydraulic system. This additional centrifugal force causes a further collapse of the spring structure I4 in the driven disc and a flexing of the cover plate with the result that the control arm 69 shifts in the slot 68 and the load exerted on the arm 69 by the piston is thereby relieved.

Let it be assumed that the vehicle was started from a standin position with the transmission gears in the box 6 set for a low gear ratio and that it is now desirable to shift in the higher gear ratio which requires clutch disengagement. The operator grasps the knob I 30 and applies pressure for shifting the gears. The arrangement is such that pressure is applied in a direction so that the knob I30 is moved to the position shown in Fig. 16 and the electrical contact established between spring I3I and contact I32. This energizes the solenoid I40. The valve is lifted as shown in Fig. 15. The pressure liquid is now transmitted through port II and line 82 to the xclutch release-side of the. clutch control piston form this function, since both the pressure and the centrifugal force increase with the square of the speed and are coordinated for this purpose.

As the control piston is thus shifted, the liquid on the clutch engagin side of the piston is displaced through line-79, port I50 and back into .the sump chamber 36 through the port I42.

After the gearshift has been made, the operator releases the-knob I30 and the electrical contact isbroken, the solenoid de-energized and thevalve restored to the position shown in Fig. 14, whereupon the pressure liquid, is transmitted through line 11, port 1111, port I50 andline 19 to, the engagement side of the piston and the liquid on the opposing side of the piston is displaced through line 82, port I5I and back to the sump through port I43. This description of clutch engagement and disengagement has been given without regard to an additional automatic control of the engine throttle in order-to first clarify the action of the clutch. control cylinder-and the flow of the pressure-liquid; 1 A j There is, however; an-automatic. engine control which takes over the control of the throttle when the clutch is, for:ex'ample, about one-third disengaged. This automatic control; takes the throttle mechanism out of thecontrol of the driver, substantially closes the throttle, so that the engine may decelerate toward idling speed and then after-the gear shift has been made and the clutch is about two-thirds engaged, the con-' trol of the throttle mechanism is restored to the driver. This is the purpose of the mechanism, largely shown in Fig. 10, and the reaction cylinder 86 as shown in Fig. 13.,

It will be observed that the reaction cylinder 86 is directly connectedto the pressure outlet 41 so that in all normal operating conditions of the pump, the piston 88 is shifted against the spring 89 and positioned in the left hand end of its cylinder. The position of the piston 88 controls the position of the sleeve, I I3 to which it-is connected through the arm 92 and therefore controls the-position of the shoulder II2 (Fig. 18). When the control piston starts to push the control arm 69 toward clutch disengagement position, the sleeve I0! is also rotated through its connection I 08 with the arm 69. The direction of rotation of sleeve I0! is such that its abutment I I0 moves in the direction of the arrow illustrated in Fig. 18, which is upwardly on the sheet of the drawings. The shoulder I I0, therefore, abuts the endIl'I of the spring clutch member H6 and starts to rotate it. But the opposite end of the spring I I8 abuts the shoulder vI I2 held positioned hydraulically by the piston 88. Only a few ounces of pressure is necessary to be applied on the .abutment II2 as this resistance is adequate for causing an expansion of the spring to establish a clutching engagement with the sleeve I20. As mentioned above this may occur when the clutch is about one-third disengaged. In the remaining two-thirds of the disengaging movement, the sleeve I20 is moved with the moving clutch mechanism, or in other words theshaft 28, and this moves the arm..I04, to which the sleeve I20 is 111 connected throughtheyi'eldabl'espringi 2 I:. This movement of the arm W4. is. counterclockwise as Fig. 9 is viewed.- As above-pointed out-the" arm 'is connected:throughlinkageshown to the throttle control lever 96. Therefore; in the-remaining two-thirds of the disengaging movement of the clutch, the throttle is moved firmly 'but strongly back toward closed position-,- which is: engine idling position, and the control treadle:pedal. 95 is likewise pushed back to engine: idling position against the weight of the foot of: the-operator. The energizing piston88 functions'to locate the abutment I I 2: in an energizing position only when there isa su-pply'of liquid under'pressure- Therefore, it is only when the driven shaft 5 is operating that the coil spring clutch becomesengaged.

When-the vehicle is standing at restIor-when it decelerates to a substantially atrest-condition the throttle is free and completely under the control of the operator.

It willv be appreciated that theclutchcontrol mechanism will. move to complete' disengaging position; Under some circumstances, the: throttle'may be onlyfpartially open when theclu'tch is disengaged and therefore doesnothave the range of movement that the-clutch mechanism has. This is the reason for the use oftthe spring I'2I. When the throttle has moved to closed position and can move no further, the clutoh 'mechanism continues. to: move toifull clutch disengagement position and the spring 'fli yields to permit of this action. In theabove action,

therotation of the springi I6 forces'rotary movement or the sleeve"- I I3 andtherefore lforees the piston. 88 to" shiftto-the: right as Fig. I3 is viewed against the pressure of the liquid; But this energizing cylinder is small and. the liquid; is merely displace'dfback' through the line 81 which: connects to the outlet 41 and outlet line TI. The hydraulic pressure on the energizingpistontil keeps the clutch spring energizedthrough this entire period. Upon clutch engagement, the parts move reversely'and whenthepiston 88 reaches the end of its movement the-abutment Itzstops while the abutment III] 'follows'the clutch engaging action and the expandin and energizing on the 'spring is discontinued. Thus the accelerator is firmly. moved back from engine idling position to substantially the original. position where' it was coupled with the-clutch operating. mechanism and then it'is' released by" the de-energization ofthe clutch spring Sand-restored to the control oflthe d'river. If for any reason, the piston'flt might Joe a: little sluggish or lag behind the clutch mechanism in clutch engaging movement, the" auxiliary-pin I26 will pick up the sleeve II3 and cause the sleeve and piston'to return to normal energizing position. This is merely a safetyifactor'. The adjustment at 9I between the piston-88 andthearm 92-established the normal position of the abutment I I2. Therefore, this'determines the point in the clutch engagement and disengagement actions where the throttle mechanism is coupled to and released from the clutch operating mechanism. As mentioned above the engagementmay take place when the clutch is about one-third disengaged and may be discontinued when the clutch is about two thirds engaged;

Accordingly, the driver of the vehicle is required only to apply pressure on the gearshift knob I30; this starts the clutch-disengaging action; the functioning of the throttle istaken 'away'irom the driver during clutch disengagement and the throttle gradually and firmly moves to closed position; when thetoperator releases? the knob, after the gear shift has been made, vthe clutch starts: its engagement; the. throttle control mechanism is'firmlymoved' back toward open position and then the control: thereof is restored. to the driver at substantially the position itwastaken away from the driver when the clutch is about two-thirds engaged.

It. will be'appa-rentthat this standardizes the control of the engine and clutch engagement and disengagement in the normal operation of a vehicle. Yet it gives to the individual-driver a Wide latitude in which to exercisehis prerogatives a'sto howhe may elect to. operate the vehicle. In other words, it is at the drivers election'at what speeds of vehiclemovement thegearshift issto be made. The driver may operate the vehicle indefinitely'in any gear regardlessofspeed. The engine may be controlled and operated, or raced whilethe vehicle is standing at rest because in the actuation ofv the throttle, the sleeve I20 freely oscillates relativeto'the coil spring. IIJS. Inother words; it is only in the course-of aclutch disengagement while the vehicle is moving that the spring I I6 is energized to causethe clutch mechanism to take over the control of the throttle.

A- mo'difiedform of control. is shown in Figs. 19 and 20. In this form of control, the clutch and the hydraulic system isthesameasthatheretorare described and the modification: relates tothe control of the throttle. Such parts as have been heretofore described and which. are the same in the modified form, bear the same referencechar acters and re-descri-ption is unnecessary. Inthis f oi'm. the accelerator treadle is shown at I 80, connected by a'link I BI to a crank having an arm I82 and a yoke shaped arm" I83. Carried theyoke on trunnions I 84*is a cylinder [Biacted upon by a retractor spring I86; Within the cylinder isa piston I 81 acted uporrby a? spring .2 88: and-the piston isconnected by a rod I89 to therthrcttle lever I913. There is no mechanical connection between this throttle control and the clutch mechanism but a pressure line 81a connects into the cylinder at I9I and this pressure line connects at I92 to the pressure-line '82 whichis the disengagement pressure line for the control cylinder 65'.

In normal operation with the clutch engaged, the liquid pressure from the pump. is applied to the control cylinder through the line I9 and there-fore there is no pressure in the line 82 or line 810. or in the cylinder I851 Therefore the spring 88 shifts'the piston I-8'I to' a normal position at the right hand end of the cylinder as Fig. 19 is viewed. This spring IB-Bhas'sufficient strength so that when the accelerator is depressed the throttle is moved toward open position'by force transmitted through cylinder I and spring I88 to the rod I 89. However, when the clutch begins disengagement, by reason of the introduction of liquid under pressure into line 82, the pressureliquid enters the cylinder I 85 and pushes the piston I81 to the opposite end of the cylinder. This shortens the coupling in the control line so that, even if the accelerator pedal I80 is pushed all the way down, the stroke of the piston is long enough to cause a movement of the throttle lever 29!! to substantially closed position; When the accelerator I8!) is released and retracted by the spring I86, the movement of the piston I81- "hy draulically will cause the spring I95 to be com pressed. Thus, although the operator may shift the accelerator pedal I80 as he desires, the throttle control isdisabled during clutch-dis- 7.13 engagement. 7 Upon clutch engagement, however, the pressure liquid in the cylinder I85 is relieved and the piston returns to its normal extended position as shown in Fig. 19 so that throttle control is re-established.

'capacityof the engine at relatively low- R. P. M.

and means operable from a member driven by the clutch and acting upon the clutch to supplement the, engagement pressure thereof.

2. A mechanism for transmitting the power of an engine such as an engine of an automotive vehicle comprising, driving friction clutch members rotatable with the engine, a drivenfriction clutch member, a driven member connected to therdriven clutch member, means normally holding theclutch members disengaged at and below engine idling speed, centrifugal means for engagingthe clutch upon acceleration of the engine above idling speed, a control member connected tothe centrifugal means for the clutch shiftable in a clutch engaging direction and in a clutch disengaging direction, actuating means operable on the control member for shifting the same, power means operable from the driven shaft, means f-or transmitting the power of said means to the actuating means, to shift the control memberin clutch engaging direction to add to the centrifugal engagement pressure of the clutch and control means operable to reverse the direction the application of the power on the actuating means to disengage the clutch against centrifugal force.

3. A mechanism for transmitting the power of an engine such as an engine of an automotive vehicle comprising, driving friction clutch members rotatable with the engine, a driven friction clutch member, a driven member connected to the driven clutch member, means normally holding the clutch members disengaged at and below engine idling speed, centrifugal means for engaging the clutch upon acceleration of the engine above idling speed, a control member connected to the centrifugal means for the clutch shiftable in a clutch engaging direction and a clutch disengaging direction, actuating means operable on the control member for shifting the same, a hydraulic system including a pump for liquid operable from the driven member, means for transmitting the pressure of the pump liquid to the actuating means to add to the clutch packing pressure and a control valve shiftable to reverse the direction of the application of the liquid pressure on the actuating member to disengage the clutch.

4. In combination, an internal combustion engine, a gear change transmission for transmitting engine torque, a centrifugal clutch of the friction type located between the engine and transmission and having centrifugal weights rotatable with the engine whereby the clutch is engaged incident to the operation of the engine, a hydraulic system including a pump for liquid operable by a member driven by the clutch, a motor operable by liquid pressure and operably connected with the clutch, a control valve between the pump and the motor for passing liquid to the motor to actuate the-motor in a direction to apply engagement pressure on the clutch, a shiftable control element for the transmission for effecting achange in the gearing and means movably mounted on the shiftable control element for shifting the same and operable upon movement relative to the shiftable control element to shift the valve to conduct the liquid tothe motor for reverse movement thereof for clutch disengagement 5. In'combination, an internal combustion engine, a gear change transmission for transmitting engine torque, a centrifugal clutch of the friction type between the engine and the transmission and. having centrifugal weights rotatable with the engine, whereby the clutch is engaged incident the operation of the engine, power means op-' erable by a member driven by the clutch, means operably connecting the power means to the clutch and normally acting upon the clutch to supplement the centrifugal force of clutch engagement when the said clutch driven member is operating, a shiftable control element for the shifting'of gears in the transmission and means movably mounted on the shiftable control ele-' ment for shifting the same and operable incident to its shift of the control element to reverse the direction of the application of power on the clutch for clutch disengagement. v

6. A mechanism for the transmission of torque comprising, a driving member, a driven member, driving and driven friction clutch members, centrifugal means on a driving clutch member for engaging the clutch upon adequate R. P. M.'of the driving member, clutch control means positively connected to the centrifugal means and shiftable in a direction for applying packing pressure to the clutch and in a direction to cause clutch disengagement, hydraulic means for acting upon the clutch control means including a liquid pump operable by the driven member, said pump being of a type wherein the pressure on the liquid afforded thereby varies with the square of the speed of rotation, so that the hydraulic pressure varies substantially uniformly with the variation of the centrifugal force, and control means operable to selectively apply the liquid pressure on the said clutch control means to add to the clutch packing pressure and reverse the direction of application on the control means to effect clutch release.

7. In combination, a driving member, a driven member, a friction clutch for coupling the members together and having centrifugal weights on the driving member for engaging the clutch, a clutch control member positively connected to the centrifugal weights and shiftable in a direction for applying packing pressure to the clutch and shiftable in a direction for disengaging the clutch, power means operable by a driven member having an element operable in a clutch engaging direction and a clutch disengaging direction, control means operable to cause movement of the element in the selected direction and a connection between the element and the clutch control member for shiftingthe clutch control member in opposite directions, said connection embodying a lost play coupling, whereby, the thrust of the element is removed from the clutch control member when the clutch is engaged incident to the increased centrifugal force upon increase of R. P. M. v i

8. In an automotive vehicle including an internal combustion engine and a driven element, a centrifugal clutch between the engine and the element having one or more driving members rota.talavle.--- withthe-engineand a-driven member .ior rotatingwtheelement, one; of, the driving members having eentrifugalxweights: thereon, the clutch amt weights beingarranged so that the clutch; is disengagedet-the. idling-R-., P. M. of the engine and so that theiclutch engages: underv the action of. centri-iugalafforceiuponr increase of the engine R19. ML-over-idling, Ra-P. M. whereby, increase of. the engine. R.,P'.* M. initiates vehiclefmovement and power means having an aotuatingqpart conneeted: to. thee-centrifugal; weights: and ,operable by thedriven element; for applying, clutch engage ingriorcesz on the centrifugal weightsand-arranged to; ;maintain the clutchenga ed. as the-' vehicle deeelerates to.- 8118138811501; movementlower than. that: which eorrespcndsitoithe-ridlingglEtP. of the engine, control means. operable to. reverse the application of the-force of ,1 the; pcwer, means on the centrifugal weights to disengage the clutch at any operating R..P. M;

9. Inan automotive. vehicleincl-nding, an, internal; combustion engine: andv a driven 1 element a centrifugal; clutch between -zthe .eng;ine and the element having; lne -ormore driving members rotatable with. the; engine and-ra-d-riven member for rotatinggtheelement, oneof the driving, mem:- bers. having; centrifugal weights thereon, the clutch andweights,being-arrangedso that the clutch is disengagedatthe-idlingR. P. of the engine and so thatathe clutch engages under the action of centrifuga-l force: upon inerea'se'of the engine R; P, M. to, initiate vehicle movement, ahydraulic: system including a pump operablegby the driven element and includinga .power1e1ement with. a, shiftabledeviceopera'bly, connected to the centrifugal we hts. to apply, centrifu al weightspackingforces on theV-clutchwhen the vehicle is moving and arranged to maintain the clutch engaged when the vehicledecelerates to a rate of speed lower than that corresponding to engineidling speed.

ERNEST E.

Regerences cited in the me, ofthis patent UNITED STI'A'IES PATENTS.

Number" Name- Date 1,80 6, l58 Giger May- 19, 1931 2,073,692 Griswold Mar. 16,1937 2,074,476 Kolb Mar. 23; 1937 2,079,822 Serra May 11, 1937 2,087,643 Gillett July 20, 1937 2,104,061 S irdy- Jan; 4', 1938 2,118,123 Watts May 24, 1938 2,144,022" Kliesrath- Jan. 17, 1939 2,153,509 Rockwell Apr. 4, 1939 2,168,682" Paine Aug-. 8,1939 2,183,481 Johnson- Dec-12,1939 2,197,480 Neill 1 Apr. 16,- 1940 2,230,050 Nutt et al. Jan. 28,1941 2,248,377 Nutt July 8, 1941 2,256,258 Flickinger Sept. 16,- 1941 2,328,090 Nutt-et a1 Aug. 31, 1943 2,328,092 Nutt et al Aug. 31, 1943 2,356,598 Lang et a1; Aug. 22, 1944 2,422,155 Wemp June 10, 1947' 2,479,532 Wemp Aug. 16,1949 

